US5113719A - Engine load responsive line pressure control arrangement for automatic automotive transmission - Google Patents

Engine load responsive line pressure control arrangement for automatic automotive transmission Download PDF

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Publication number
US5113719A
US5113719A US07/363,261 US36326189A US5113719A US 5113719 A US5113719 A US 5113719A US 36326189 A US36326189 A US 36326189A US 5113719 A US5113719 A US 5113719A
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United States
Prior art keywords
engine
line pressure
load
transmission
rate
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US07/363,261
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English (en)
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Yutaka Suzuki
Masayuki Kobayashi
Tatsuo Wakahara
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Nissan Motor Co Ltd
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Nissan Motor Co Ltd
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Assigned to NISSAN MOTOR CO., LTD. reassignment NISSAN MOTOR CO., LTD. ASSIGNMENT OF ASSIGNORS INTEREST. Assignors: KOBAYASHI, MASAYUKI, SUZUKI, YUTAKA, WAKAHARA, TATSUO
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
    • F16H61/0021—Generation or control of line pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
    • F16H61/04—Smoothing ratio shift
    • F16H61/0437—Smoothing ratio shift by using electrical signals
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
    • F16H61/02—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing characterised by the signals used
    • F16H61/0202—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing characterised by the signals used the signals being electric
    • F16H61/0251—Elements specially adapted for electric control units, e.g. valves for converting electrical signals to fluid signals
    • F16H2061/0255—Solenoid valve using PWM or duty-cycle control
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H59/00—Control inputs to control units of change-speed-, or reversing-gearings for conveying rotary motion
    • F16H59/14—Inputs being a function of torque or torque demand
    • F16H59/141—Inputs being a function of torque or torque demand of rate of change of torque or torque demand
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H59/00—Control inputs to control units of change-speed-, or reversing-gearings for conveying rotary motion
    • F16H59/14—Inputs being a function of torque or torque demand
    • F16H59/24—Inputs being a function of torque or torque demand dependent on the throttle opening

Definitions

  • the present invention relates generally to an automatic transmission for use in automotive vehicles and more specifically to a line pressure control arrangement for such a transmission which maintains an adequate amount of friction element engagement during modes of operation when a sudden reduction in engine load occurs.
  • An automatic transmission Service Manual (publication A261C07) issued in March 1987 by the Nissan Motor Company relating to the so called RE4RO1A type transmission, describes an arrangement which utilizes tabled data for controlling the line pressure in response to engine load during shifting and non-shifting modes of transmission operation.
  • the engine throttle valve opening degree is used to determine the duty cycle of a signal which is used to control a line pressure control solenoid valve.
  • the first is such that under stall conditions, when the accelerator pedal is released, the intertia torque is larger than the torque actually being produced by the engine. Nevertheless, the level of line pressure is controlled in response to the throttle opening degree and is according suddenly reduced with the rapid closure of the throttle valve. The amount of engagement of the friction elements becomes lower than suited for handling the reverse flowing inertia torque and the jitter occurs.
  • the line pressure tends to closely parallel the throttle opening as indicated in the solid line trace in FIG. 6C.
  • the torque smoothly decreases from a peak value while the line pressure drops to a level which is inadequate to handle the amount of torque being outpulled by the engine and as a result jitter is again encountered.
  • the above object is achieved by an arrangement wherein, when the load on the engine of an engine/transmission system reduces suddenly, this sudden reduction is used as a trigger to delay the reduction of the line pressure which is supplied to the friction elements of the transmission in a predetermined manner which allows for engine speed/torque output to actually drop to the same level as the load.
  • a first aspect of the present invention is deemed to comprise a line pressure control system for an automatic automotive transmission which features: means for selectively controlling the level of line pressure in response to changes in the load applied to the engine of an engine operatively connected with the transmission; means for detecting the rate at which the load on the engine is changing; and means for delaying the reduction in line pressure in response to rapid reductions in the engine load.
  • a second aspect of the present invention is deemed to comprise a line pressure control system for an automatic automotive transmission which features: means for selectively controlling the level of line pressure in response to changes in the load applied to an engine which is operatively connected with the transmission; means for sensing the rotational speed of the engine; means for sensing the rotation speed of the output shaft of the transmission; means for detecting the rate at which the load applied to the engine is changing; and means for delaying the reduction in line pressure in response to rapid reductions in the load applied to the engine and in accordance with the sensed rotational engine speed.
  • a third aspect of the invention is deemed to comprise a vehicle which features: an internal combustion engine; a transmission, the transmission being operatively operated with the internal combustion engine; a load sensor, the load sensor being arranged to sense the load on the engine and produce a signal indicative of the same; a source of line pressure which supplies hydraulic fluid under pressure to a plurality of friction elements, the friction elements being selectively engageable to produce a plurality of gears; a line pressure control solenoid, the line pressure solenoid being arranged to be operated by a control signal the duty cycle of which is selectively variable; a memory in which a line pressure control schedule is stored, the line pressure control schedule being recorded in terms of duty cycle and throttle position; a control circuit, the control circuit being responsive to the load sensor, operatively connected with the memory and arranged to produce the control signal, the control circuit including: first means responsive to the signal indicative of load for determining the rate at which the load on the engine is changing; and second means for modifying the control signal in the event that the first means indicates that the the load on
  • a fourth aspect of the invention is deemed to comprise a vehicle which features: an engine, the engine having a throttle valve; a transmission, the transmission being operatively operated with the internal combustion engine, the transmission having an input shaft and an output shaft; a load sensor, the load sensor being arranged to sense the position of the throttle valve; a plurality of friction elements, the friction elements being selectively engageable to produce a plurality of gears; a source of line pressure which supplies hydraulic fluid under pressure; a line pressure control solenoid, the line pressure solenoid being arranged to be operated by a control signal the duty cycle of which is selectively variable; a memory in which line pressure control data is stored, the line pressure control data comprising: a line pressure control schedule, the line pressure control schedule being recorded in terms of duty cycle and throttle position; a control circuit, the control circuit being responsive to the load sensor, the control circuit being operatively connected with the memory, the control circuit being arranged to produce the control signal, the control circuit including: first means for determining the rate at which the load on the engine is changing
  • a fifth aspect of the present invention is deemed to comprise a method of controlling the level of line pressure in an automatic transmission which features the steps of: determining the load on engine operatively connected with the the transmission; controlling the level of line pressure in accordance with the load on the engine; detecting the rate at which the load on the engine is reducing being above a predetermined level; and delaying the reduction in the line pressure in the event that the load on the engine reduces at a rate above the predetermined one.
  • FIG. 1 is a diagram showing the concept of the line pressure control according to the present invention
  • FIG. 2 is a diagram showing the system which embodies a first embodiment of the present invention
  • FIG. 3 is a flow chart showing the characterizing operations which are performed by a control routine according to the first embodiment of the present invention
  • FIG. 4 is a chart showing in terms of time and throttle valve opening the line pressure control characteristics which are provided by the first embodiment of the present invention
  • FIG. 5 is a flow chart depicting the operations which are performed in accordance with a second embodiment of the present invention.
  • FIG. 6 is a timing chart which shows the control characteristics achieved with the second embodiment of the present invention.
  • FIG. 7 is a diagram showing the system utilized in a third embodiment of the present invention.
  • FIG. 8 is is a flow chart which depicts the characteristic operations produced by the third embodiment of the present invention.
  • FIG. 9 is a timing chart showing the control characteristics produced by the third embodiment.
  • FIG. 10 is a flow chart which depicts the operations performed in accordance with a fourth embodiment of the present invention.
  • FIG. 11 is a timing chart which shows the control characteristics produced by the fourth embodiment.
  • FIG. 12 is a chart which compares, in terms of throttle (and pseudo throttle opening) and duty cycle (and line pressure) the normal line pressure variation characteristics, with those produced by the present invention.
  • FIG. 2 shows a system which embodies a first embodiment of the present invention.
  • an automatic transmission 1 of the so called RE4RO1A type described in Service Manual (publication A261C07) issued in March 1987 by the Nissan Motor Company is operatively connected with an internal combustion engine 2 by way of a torque converter (no numeral).
  • First and second shift solenoids 3 and 4 and a line pressure control solenoid 5 are operatively connected with a valve body 6.
  • line pressure is supplied to the friction elements of the transmission in a manner to selectively produce first to fourth forward speeds.
  • the level of the line pressure which is supplied to the friction elements is controlled by the duty cycle of the signal which is applied to the line pressure control solenoid 5.
  • the level of line pressure is arranged to decrease with the increase in duty cycle and vice versa.
  • a control unit 7 which includes a microprocessor is arranged to receive data input from a engine throttle position sensor 8 and a vehicle speed sensor 9. Using this data the control unit determines which gear the transmission should be conditioned to produce and determines the appropriate energization pattern for the shift solenoids. The appropriate level of line pressure is also determined in accordance with the data inputted from the throttle valve position sensor 8.
  • FIG. 3 depicts in flow chart form the steps which are executed by a control routine.
  • the control routine is arranged to be run at predetermined time intervals ⁇ T.
  • ⁇ T can be set at 10 msec.
  • the first step 20 of this routine is such as to read the instant values of throttle position TH and vehicle speed V and set these in memory for further processing.
  • the change ⁇ TH is determined by subtracting the instant TH value with that TH(OLD) which was recorded on the previous run of the routine.
  • step 22 it is determined if the value of TH has decreased. In the event that ⁇ TH ⁇ 0 then the routine flows across to step 24 wherein the TH(OLD) value is updated via recording of the instant TH value at its memory address.
  • step 23 the routine goes to step 23 wherein the absolute change
  • a pseudo throttle value TH(IM) is determined by subtracting the value of K from the instant TH(OLD).
  • Steps 24 and 25 are such as to update the value of TH(OLD) and to determined the line pressure duty cycle valve D in accordance with the instant value of TH.
  • valve of TH(OLD) is updated via the recording of the TH(IM) value at its memory address and at step the value of TH(IM) is used to determine the duty cycle of the signal which is applied to the line pressure control throttle valve 5.
  • steps 27 and 28 are such as to decrement the throttle value TH(IM) by an increment K per run of the control routine while the actual amount of closure per run is greater than K. Accordingly, the rate at which the line pressure is decreased is controlled to a predetermined rate and not in accordance with the rate at which the actual throttle valve position is closing.
  • the line pressure is gradually reduced under the control of the pseudo throttle opening value TH(IM) and not permitted to drop so rapidly as to bring about the situation wherein the level of line pressure is insufficient for the instant torque transmission conditions.
  • step 26 a signal having the duty cycle determined in step 29 is issued to solenoid 5.
  • Steps 26 to 33 relate to the setting of the shift solenoids 3 and 4 in accordance with the instant set of engine load and vehicle speed conditions.
  • step 30 the gear in which the transmission should be set for the instant set of V and TH values is determined. Following this at step 31 the instant gear the transmission is conditioned to produce is compared with the one determined in step 30. In the event that the two gears are the same the routine by-passes step 32 and goes directly step 33 wherein commands which maintain the instant set of solenoid energizations are issued.
  • step 32 the change which is required and the manner in which the change should be implemented is determined. This determination of course involves the determination of solenoid energization pattern or patters which should be effected to being about the required transmission shift.
  • FIG. 5 shows the control routine which is implemented in accordance with a second embodiment of the present invention.
  • the flag has not been set then at steps 22 and 41 the magnitude of ⁇ TH and the vehicle speed are sequentially checked. That is to say, in the event that ⁇ TH is found to be less than 0 (indicative of the throttle valve closing) the instant speed is checked to determine if it is below a predetermined value Vs (where Vs is a relative small value) or not.
  • step 44 the flag FLG is set and at step 45 the count of a soft timer TM is incrementally increased.
  • Steps 26, and 30-33 are the same as the corresponding steps described in connection with the flow chart shown in FIG. 3.
  • the routine is arranged to flow to steps 42 and 25 in the event that the throttle valve is found to be either stationary of opening ( ⁇ TH is equal to or greater than 0), the vehicle speed is equal to or greater than Vs, or the count of timer TM has exceeded To.
  • step 42 flag FLG and the soft clock timer TM are cleared and in step 25 the instant value of TH is used directly to control the line pressure.
  • TH(IM) the value of TH(IM) remains constant for time To and as shown by chain line in FIG. 6(A) the line pressure is accordingly maintained as shown in chain line in FIG. 6C.
  • FIG. 7 shows an engine/transmission system to which third and fourth embodiment of the invention is applied.
  • this system is essentially the same as the arrangement shown in FIG. 2 and further features the provision of an engine speed sensor 10.
  • the instant ⁇ TH is compared with a predetermined value - ⁇ THs which is indicative of throttle closure which accompanies sudden deceleration and the instant engine speed Ne is compared with a given value Neo.
  • the value of Neo is a value which is set in accordance with the selected gear of the transmission.
  • step 44 flag FLG is set and at step 52 the value of the duty cycle D is set to a predetermined value Ds.
  • the values of Neo and Ds are set in the manner shown in FIGS. 9A and 9B. Accordingly, with the control provided by the above steps, the duty cycle is held at Ds until such time as the engine speed drops to Neo.
  • the routine flows to steps 53 and 25 wherein the flag FLG is cleared and the duty cycle determined in accordance with the instant throttle opening value TH.
  • Steps 26 and 30 to 33 are as described previously.
  • FIG. 10 shows the control routine which characterizes a fourth embodiment of the present invention. This embodiment produces the line pressure control indicated by the broken line in FIG. 11.
  • this program is essentially the same as that depicted in FIG. 3 and is arranged so that a new step 60 is introduced between steps 23 and 28 and arranged to follow step 51 wherein the engine speed is compared with the predetermined value Neo.
  • TH(IM) is derived by reducing the value of TH(OLD) by an engine speed dependent increment K(Ne).
  • TH(IM) is therefore incrementally decreased each run of the program until such time as the engine speed drops to Neo whereat the amount of torque which is delivered from the engine via the torque converter is sufficiently low that the level of the line pressure can be dropped to its minimum value without any slippage of the like occurring.
  • the rotational speed of the transmission input shaft is also monitored and used in combination with the vehicle speed signal (taken in this embodiment from the rotational speed of the transmission output shaft) and used to develop a gear ratio which can be used to control the setting of the solenoid energizations.
  • shifting is controlled in response to solenoid operation and can be applied to other types of transmission wherein shifting (merely by way of example) is controlled in response to throttle and governor pressures which are developed by mechanically operated valves.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
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US07/363,261 1988-06-08 1989-06-08 Engine load responsive line pressure control arrangement for automatic automotive transmission Expired - Lifetime US5113719A (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP63139232A JP2581762B2 (ja) 1988-06-08 1988-06-08 自動変速機のライン圧制御装置
JP63-139232 1988-06-08

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EP (1) EP0360980B1 (fr)
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DE (1) DE68908822T2 (fr)

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5163342A (en) * 1992-04-03 1992-11-17 General Motors Corporation Adaptive transmission pressure control with run-through detection
US5317937A (en) * 1991-09-14 1994-06-07 Honda Giken Kogyo Kabushiki Kaisha Control system for vehicle automatic transmission
US5558384A (en) * 1993-08-04 1996-09-24 Giat Industries Motorized breakdown vehicle
US5665028A (en) * 1994-02-23 1997-09-09 Nissan Motor Co., Ltd. Shift capacity control for automatic transmission
US5759134A (en) * 1995-07-25 1998-06-02 Mazda Motor Corporation Control system for automatic transmission
US5842953A (en) * 1996-07-10 1998-12-01 Toyota Jidosha Kabushiki Kaisha Automotive vehicle lock-up clutch control apparatus wherein change of line pressure for lock-up clutch slip control valve is restricted during slip control mode
US20040005956A1 (en) * 2002-07-08 2004-01-08 Beong-Yeol You Hydraulic control system for an automatic transmission

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP3468051B2 (ja) * 1997-09-04 2003-11-17 アイシン・エィ・ダブリュ株式会社 自動変速機の油圧制御装置
JP2002323125A (ja) * 2001-04-26 2002-11-08 Jatco Ltd 自動変速機のライン圧制御装置
JP4683033B2 (ja) * 2007-10-22 2011-05-11 トヨタ自動車株式会社 無段変速機を含む駆動機構の制御装置

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4296652A (en) * 1978-07-22 1981-10-27 Volkswagenwerk Aktiengesellschaft Hydraulic control for an automatic vehicle transmission
EP0047517A2 (fr) * 1980-09-04 1982-03-17 Nissan Motor Co., Ltd. Système de contrôle pour pression hydraulique d'une transmission automatique pour réduire les à-coups
US4324156A (en) * 1978-09-29 1982-04-13 Nissan Motor Company, Limited Method and apparatus for hydraulic control of automatic transmission
US4331045A (en) * 1978-08-01 1982-05-25 Volkswagenwerk Aktiengesellschaft Pneumatic control system for an automatic vehicle transmission
US4347764A (en) * 1978-09-23 1982-09-07 Ford Motor Company Hydraulic control valve system for a planet gear transmission particularly for motor vehicles
US4350234A (en) * 1979-02-02 1982-09-21 Nissan Motor Co., Ltd. Automatic transmission system provided with a function of engine brake
US4354236A (en) * 1979-02-14 1982-10-12 Aisin-Warner Kabushiki Kaisha System for controlling the hydraulic pressure during a shift operation of an automatic, variable speed transmission
US4394827A (en) * 1980-03-27 1983-07-26 Toyota Jidosha Kogyo Kabushiki Kaisha Transmission control system with modified friction engaging mechanism actuating pressure
US4428258A (en) * 1980-03-27 1984-01-31 Toyota Jidosha Kogyo Kabushiki Kaisha Transmission control system with modified back pressure accumulator
US4563918A (en) * 1983-07-29 1986-01-14 Nissan Motor Co., Ltd. Line pressure control of hydraulic control system for automatic transmission
EP0234685A2 (fr) * 1986-02-03 1987-09-02 General Motors Corporation Commande de montée de rapport par embrayages
US4724724A (en) * 1986-01-08 1988-02-16 Fuji Jukogyo Kabushiki Kaisha System for controlling line pressure of a continuously variable transmission for a motor vehicle

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4283970A (en) * 1979-07-02 1981-08-18 General Motors Corporation Automatic transmission line pressure control
JPS6262052U (fr) * 1985-10-08 1987-04-17

Patent Citations (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4296652A (en) * 1978-07-22 1981-10-27 Volkswagenwerk Aktiengesellschaft Hydraulic control for an automatic vehicle transmission
US4331045A (en) * 1978-08-01 1982-05-25 Volkswagenwerk Aktiengesellschaft Pneumatic control system for an automatic vehicle transmission
US4347764A (en) * 1978-09-23 1982-09-07 Ford Motor Company Hydraulic control valve system for a planet gear transmission particularly for motor vehicles
US4324156A (en) * 1978-09-29 1982-04-13 Nissan Motor Company, Limited Method and apparatus for hydraulic control of automatic transmission
US4350234A (en) * 1979-02-02 1982-09-21 Nissan Motor Co., Ltd. Automatic transmission system provided with a function of engine brake
US4354236A (en) * 1979-02-14 1982-10-12 Aisin-Warner Kabushiki Kaisha System for controlling the hydraulic pressure during a shift operation of an automatic, variable speed transmission
US4394827A (en) * 1980-03-27 1983-07-26 Toyota Jidosha Kogyo Kabushiki Kaisha Transmission control system with modified friction engaging mechanism actuating pressure
US4428258A (en) * 1980-03-27 1984-01-31 Toyota Jidosha Kogyo Kabushiki Kaisha Transmission control system with modified back pressure accumulator
EP0047517A2 (fr) * 1980-09-04 1982-03-17 Nissan Motor Co., Ltd. Système de contrôle pour pression hydraulique d'une transmission automatique pour réduire les à-coups
US4563918A (en) * 1983-07-29 1986-01-14 Nissan Motor Co., Ltd. Line pressure control of hydraulic control system for automatic transmission
US4724724A (en) * 1986-01-08 1988-02-16 Fuji Jukogyo Kabushiki Kaisha System for controlling line pressure of a continuously variable transmission for a motor vehicle
EP0234685A2 (fr) * 1986-02-03 1987-09-02 General Motors Corporation Commande de montée de rapport par embrayages

Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5317937A (en) * 1991-09-14 1994-06-07 Honda Giken Kogyo Kabushiki Kaisha Control system for vehicle automatic transmission
US5163342A (en) * 1992-04-03 1992-11-17 General Motors Corporation Adaptive transmission pressure control with run-through detection
US5558384A (en) * 1993-08-04 1996-09-24 Giat Industries Motorized breakdown vehicle
US5665028A (en) * 1994-02-23 1997-09-09 Nissan Motor Co., Ltd. Shift capacity control for automatic transmission
US5759134A (en) * 1995-07-25 1998-06-02 Mazda Motor Corporation Control system for automatic transmission
US5842953A (en) * 1996-07-10 1998-12-01 Toyota Jidosha Kabushiki Kaisha Automotive vehicle lock-up clutch control apparatus wherein change of line pressure for lock-up clutch slip control valve is restricted during slip control mode
US20040005956A1 (en) * 2002-07-08 2004-01-08 Beong-Yeol You Hydraulic control system for an automatic transmission
US6832977B2 (en) * 2002-07-08 2004-12-21 Hyundai Motor Company Hydraulic control system for an automatic transmission

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Publication number Publication date
EP0360980A1 (fr) 1990-04-04
JP2581762B2 (ja) 1997-02-12
JPH01312253A (ja) 1989-12-18
DE68908822T2 (de) 1993-12-09
DE68908822D1 (de) 1993-10-07
EP0360980B1 (fr) 1993-09-01

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